Press



April 24, 1951 R. w. GLASNER ET AL 8 Sheets-Sheet 1 Filed Oct. 19, 1949 Aprii 1951 R. w. GLASNER ET AL. 2,550,061

PRESS 8 Sheets-Sheet 2 Filed 001;. 19, 1949 8 Sheets-Sheec 3 PRESS R. W. GLASNER ET AL April 24, 1951 Filed Oct. 19, 1949 llig v k k 9 r April 24, 1951 R. W. GLASNER ET AL PRESS 8 Sheets-Sheet 4 Filed Oct. 19, 1949 1% W W%@ M W:

April 24, 1951 R. w. GLASNER ET AL PRESS 8 Sheets-Sheet 5 Filed Oct. 19, 1949 mu 4 7/ w /f m April 24, 1951 R. w. GLASNER ET AL 2,550,061

PRESS Filed Oct. 19, 1949 8 Sheets-Sheet 6 xii @067? 0/15. [6 05077 5/6157267 ZZzarflfi/a/zanaezz PRESS 8 Sheets-Sheet 7 Filed Oct. 19, 1949 Patented Apr. 24, .1951

PRESS Rudolph W. Glasner, Chicago, and Einar K. Johansen, Oak Park, Ill., assignors to Clearing Machine Corporation, Chicago, 111., a corporation of Illinois Application October 19, 1949, Serial No. 122,208

6 Claims.

This invention relates in general to presses of the type for forming, shaping, or drawing sheet metal, and particularly to mechanically operated presses for performing such functions. More specifically, the invention relates to mechanically operated presses of the so-called double action type.

Mechanically operated metal drawing presses of the double-action type as presently used employ an outer slide or blank holder which clamps a sheet metal blank or work piece, and an inner slide which forms, draws or shapes the sheet metal blank after it has been clamped in position by the outer clamping slide. These present presses have proven very satisfactory in general, but they have the disadvantage in that they are unable to produce the desired production quantity principally because the number of operating cycles per period of time is limited. The inadequacy of the number of operations or operating cycles per period of time retards the production line and, therefore, limits and prevents rapid production. The reasons for the lack of more rapid production because of the limited number of cycles of operation within a given time limit is due to the construction, position and arrangement of the parts. These prior mechanical presses are ordinarily operated by a crank or eccentric, and the forming or drawing of the sheet metal must be consistent with the type of sheet metal which is now available. The present available sheet steel ordinarily has an approximate drawing or flowing speed of about sixty feet per minute; therefore, the actual speed of drawing sheet steel is limited by the flowing or draw speed of the metal. Should the draw speed of the metal be increased, the sheet metal would fracture, break or otherwise prevent a proper metal draw.

Conventional mechanical crank operated metal presses, therefore, have the disadvantage in that the throw of the crank determines the depth of the draw, or the depth of the draw to be performed on the metal determines the throw of the crank to be used. For instance, should a metal draw of twelve inches be required, the vertical movement of the inner or draw slide must be at least twenty-four inches, plus an additional amount to permit the finished drawn metal or article to be withdrawn from the dies. draw slide must move twelve inches from the point it first engages the blank to finish the twelve inch draw. The draw slide must then be raised twelve inches to withdraw it from the finished piece where it will be at the same point where the metal drawing operation began. It is then The metal necessary to raise the draw slide an additional twelve inches so that the finished or drawn sheet may be withdrawn from the press. Of course, there must be more than twenty-four inches overall travel so that the finished drawn piece may be withdrawn freely from the press. In any event, the metal drawing slide must have at least a twenty-four inch travel or movement for a twelve inch metal draw. The crank which operates a draw slide to form a twelve inch draw must necessarily have at least a twenty-four inch stroke, and inasmuch as the crank rotates and the crank connections operate in a circular path, the actual circumference of the circle about which the crank connection travels, will be diameter times pi (Z 3.1416-) or approximately 6.2832 feet. The drawing speed of sheet steel as used at the present time having an approximate speed of only sixty feet per minute, the movement of the crank must be limited in speed according to the maximum drawing speed of the metal, viz., sixty feet per minute. Therefore, to effect a twelve inch draw, the peripheral rotative speed of the crank will be 6.2832 feet per minute. Because the maximum metal drawing speed of the metal is limited to approximately sixty feet per minute, the numer of cycles that the machine can perform with a crank of this given size is divided by 6.2832 or approximately nine and onehalf (9.54) cycles per minute.

Being limited by the length of the depth of the draw, and the speed at which metal may be drawn, the crank must have a proportional throw, and, therefore, it is impossible to increase the production rate of the present crank-operated presses.

The present invention has to do with increased production of metal drawn articles without increasing the actual drawing speed of the metal, the metal drawing operation still being limited by the conventional type of sheet steel available which has an approximate drawing speed of sixty feet per minute.

The primary object of the present invention, therefore, is to maintain the present drawing speed to which sheet steel is limited, but to provide a new system of operating mechanism to effect a greater number of cycles of operation of a mechanical press over a given period of timev A further object of the invention is the provision of new and improved mechanism for a double acting press whereby the operating mechanisms for the slides are interconnected and corelated to effect simultaneous travel of both slides to the point of clamp holding position of the outer slide, and then to maintain the outer slide in its clamping position while the inner slide is moved independently to affect the draw, and then to withdraw both slides from operation and then later to move both slides simultaneously to their original positions.

A further object of the invention is the provision of new and improved means for operating the primary draw slide and the clamping or blank holding slide, the primary draw slide having a metal drawing speed not exceeding the maximum drawing speed of the metal but increasing the number of operating cycles per minute over conventional mechanically operated double acting presses.

A still further object of the invention is the provision of new and improved mechanism for operating a mechanical press so as to increase the number of cycles of operation of the, metal drawing slide for a given period of time and still not exceed the maximum drawing speed of the metal blank and so as to permit the bed of the press to be maintained at its. usual lower position, with the draw slide and clamp slide operating above the press bed, whereby the finished and completed drawn article may be withdrawn from the press in the usual manner without inverting the dies.

A still further object of the invention is the provision of new and improved mechanism for operating the draw slide of a. mechanical press so as to increase the number of operating cycles per minute by reducing the usual effective vertical movement of the draw slide by eliminating the ordinary crank throw employed in connection with the conventional crank type operated draw slide.

Still another object of the present invention resides in the arrangement, of the mechanisms for operating the draw slide and the clamp slide by the attachment of the slide operating mechanisms to a common movable member instead of attaching the mechanisms to a stationary cross head such as, is usually employed and located in the crown of themachine' frame.

Another object of the invention resides in the provision of a plurality of interconnected properly corelated and synchronized elements cooperating with both the inner or primary draw slide and the outer or clamping slide to effect faster reciprocation of both slides simultaneously to a given point and then reducing the speed of the inner or primary draw slide to effect the drawing or forming operation in accordance with limits not to exceed the actual drawing speed of the metal being drawn.

Another, and very important object of the invention, is the provision of a novel press construction which eliminates the usual clutch mechanisms for bringing the slides into operation; also the provision of operating the individual slides from the same single source of power, there being but a single motor to drive both slides; moreover there is provided a. mechanical interlock between the slide connecting links to prevent the slides from operating out of proper timed relationship with each other.

Numerous other objects. and advantages will be apparent throughout the specification which follows:

The accompanying drawings illustrate a certain selected embodiment of the invention and the views therein are as follows:

Fig. 1 is a detail longitudinal vertical sectional view of the press of the present invention show- 4 ing the outer clamp slide and the inner draw slide at their extreme upper positions, the view being taken on the line li of Fig. 2, parts being broken away for the sake of clearness;

Fig. 2 is a detail top plan view;

Fig. 3 is a detail sectional view on the line 33 of Fig. 2;

Fig. 4 is a detail vertical sectional view on the line t-fl of Fig. 1;

Fig. 5 is a detail horizontal sectional View on the line 5-5 of Fig. 1;

Fig. 6 is a detail horizontal sectional view on the line 65 of Fig. l

Fig. '7 is a detail horizontal sectional view on the line 'il; of Fig. 1;

Fig. 3. is. a developed sectional plan view of the outer slide linkage, the linkage being spread out in a straight line to show the various link parts and the, manner in which they are connected;

Fig. 9 is a detail longitudinal sectional view, similar to Fig. l, but showing the outer clamp slide linkage mechanism when the outer clamp slide is in its. lowermost position and clamping the blank, the inner draw slide linkage being shown in its corresponding position in dotted lines at the time the outer. slideis in clamping position with the sheet or blank, certain parts being broken away for the sake of clearness;

Fig. 10 is a detail, perspective view of interconnecting linkage between the clamp and draw slides, and the manner in whichthe outer clamp slide mechanism and inner draw slide mechanism are operatively connected. or tied together;

Fig. 11 is a detail longitudinal sectional view, similar to Fig. l, but showing the inner draw slide linkage mechanism when the inner slide is at its extreme lowermost position at the conclusion of the metal drawing or forming, operation, certainparts being omitted for the-sake of clearness, and

Figs. 12 and 13 are comparative motion curves showing the operation of two presses; Fig. 12. showing the operation of a conventional double action press, and Fig. 13 showing the operation of the double action press. of the invention.

The double action. mechanical press. herein shown for the purpose of illustrating and describing the present invention comprises a. main supporting structure or main. frame I including a base or bed 2' and strengthening wall sections 3, Figs. 1, 4, 5;, 9 and 11. A. main drive shaft d, Fig. 5, is. supported in suitable bearings carried by a part of. the main supporting struc ture I. This main drive shaft. i, is driven in any suitable manner such as. by belts 5. trained over a pulley 6,. on the shaft 4, and a pulley l on the motor shaft 8 of an, electric motor 9.

The main drive shaft 4-, Fig. 5, carries a gear H) which meshes. with, and drives, a gear II on a transverse driven shaft 1.2-, the shaft I2 being journaled in suitable bearings in the mainframe and the frame walls. Drivev gears [3,, 14, I5 and it are fixed to the rotatable driven shaft i2 and mesh with gears iglsh ill, 59: and 2.9; respectively on a second driven shaft. 24; which is. arranged adjacent the drivenshafit Hand in. parallel driving relationship therewith.

The second driven shaft 21', like the first driven shaft I2, is rotatablymounted in suitable bearings carried by the main machine frame and the frame walls.

Rotation of the motor shaft 8, therefore, causes rotation of the shafts l2 and 2|, but in opposite directions, the shaft l2. rotating in a clockwise direction, and the-shaitZl. rotating in a counter-\ clockwise direction as shown by the directional arrows in Fig. 1.

A main shaft 22 is suitably carried and supported by the frame and is in close proximity to the shaft l2 and in parallel relationship therewith, the main shaft 22 being located to the left of the shaft I2 when viewing Figs. 1, 5, 9 and 11. This main shaft 22 has outer slide bull gears 23, 24 mounted near the ends of the main shaft 22, the gears 23 and 2d meshing respectively with the gears i3 and it on the driven shaft I2, Fig. 5. The shaft I2 is driven in a clockwise direction, and, therefore, the gears 23 and 24 on the main shaft 22 will rotate in a counter-clockwise direction.

A second stationary main shaft 25 is located adjacent the driven shaft 2!, and is also suitably carried by the main frame and frame walls. The main shaft 25 is parallel to the driven shaft 2|, and is located to the right thereof in viewing Figs. 1, 5, 9 and 11. This stationary shaft 25 carries rotatably mounted outer slide bull gears 26 and 2'5 which are located near the outer ends of the main shaft 25 and mesh respectively with the gears I1 and 25 on the shaft 2!, Fig. 5. The shaft 2 i, being driven in a counter-clockwise direction, therefore, rotates the outer slide gears 25 and 2? in a clockwise direction.

The outer slide bull gears'23 and 24 on the main shaft 22, have outer slide eccentrics 28 and 29, respectively, which are rotatably mounted on the shaft 22, and the bull gears 25 and 2? on the second main shaft 25 carry eccentrics 35 and 3 l respectively, which are rotatably mounted on the main shaft 25, Fig. 5. The eccentrics 28, 28, 3B and 3! carry eccentric straps 32, 33, 34 and 35, respectively, which operate certain outer slide linkage mechanism 55 for the outer slide connection links 3? of an outer slide 35. There is one such outer slide linkage mechanism 36, and one such outer slide connection link 37 at each of the four corners of the press making a total of four such outer slide linkage mechanisms 36, and four such outer slide connection links 3? to reciprocate the outer or clamp slide 38 vertically in the main machine frame l, Figs. 1, 5 and 9.

The main shaft 22 has inner slide bull gears 39 and 45 rotatively mounted thereon between the outer slide gears 23 and 25. The gears 38 and 25 mesh with the gears I l and 35 respectively, on the driven shaft I2 and are driven thereby.

The main shaft 25 carries rotatively mounted inner slide bull gears 45 and 42 which are positioned between the outer slide gears 26 and 2'1. The gears ll and 42 mesh with the gears l5 and I 9 on the driven shaft 2| and are driven thereby.

The bull gears 35 and 55 on the main shaft 22, and the bull gears ll and 52 on the second main shaft 25, drive eccentrics 153, 44, 45 and 25, respectively, which are rotatively mounted on the respective main shafts 22 and 25. The eccentrics 43, d4, 45 and 55 operate and drive eccentric straps 4T, 58, 49 and 55, respectively, which operate certain inner or draw slide linkage mechanism 5| for the inner draw slide connection links 52 of an inner draw slide 53. There is one such inner slide linkage mechanism 5i, and one such inner slide connection link 52 at each of the four corners of the inner slide, making a total of four such inner slide linkage mechanisms 5|, and four such inner draw slide connection links 52 to reciprocate the inner or draw slide 53 vertically in the main frame, Figs. 1, 5 and 11.

Outer slide 38 and linkage operating mechanism 36' The outer or clamp slide 38, Figs. 1, 4 and 9, is operated by certain linkage mechanism 36, Figs. 1, 5 and 9, to cause the vertical reciprocation of the outer slide connection links 3! to reciprocate the outer or clamp slide 38. Each linkage mechanism 36, Figs. 1, 5 and 9, for each link 5i comprises a bell crank 54 which is pivotally mounted on a stationary rocker pin or stud shaft 55. One end of the bell crank 54 is pivotally connected at 55 to an outer slide eccentric strap, Figs. 1 and 9. The other end of the bell crank 54 is pivotally connected at 5! to a link 58. The link 58 is pivoted at 59 to one arm of a bell crank 60 which is mounted on a stationary shaft 5|. The other arm of the bell crank 60 is pivotally connected at 62 to one end of a link 63. The other end of the link 53 is pivotally connected at 54 to one arm of a bell crank 55. The bell crank 65 is pivotally mounted on a stationary shaft 66. The other arm of the bell crank 65 is pivotally connected at 67 to one end of a connecting link 58. The other end of the connecting link 68 is pivotally connected at 59 to one arm of a bell crank it], which is pivotally mounted on a stationary shaft H and rocks about this shaft H. The other arm of the bell crank 10 is pivotally connected to the lower end of an outer slide connection link 3'! by means of outer slide connection link pin l2, Fig. 9. The upper end of each outer slide connection link 37 is pivotally mounted on a pivot pin 13 carried by the outer clam-ping slide 38, Figs. 1, 4 and 9.

The linkage mechanism 35 for each connecting link 3?, from the point where the link 3'! connects to the bell crank 72, up to the point 55 where the bell crank 55 pivotally connects at 55 to an outer slide eccentric operating strap, is identical, there being linkage mechanism 35 connected to each eccentric strap 32, 33, 34 and 35 to operate a respective outer slide connecting link 37, Figs. 1, 5 and 9. Each linkage mechanism 36 is identical in construction, there being two such linkage mechanisms 35 on the right hand side of the press, and two such linkage mechanisms 35 on the left hand side of the press, Fig. 5. The positioning of right and left hand linkage mechanisms 35 is clearly shown in Fig. 9. These right and left hand linkage mechanisms 35 are duplicated, there being one pair at the front and one pair at the rear, Fig. 5. The size, shape, construction and pivotal connections of the parts forming the linkage mechanisms 35, from the point where the outer slide connection links 37 connect at 55 to its respective eccentric strap is all identical; therefore, the linkage mechanism 35 having been described in connection with one outer connection link 3?, it is unnecessary to describe again the other linkage mechanisms 36 which operate the other outer slide connection links 3'5.

Operation of the main drive shaft 5 rotates the driven shafts i2 and 2! which turn rotate the gears 25 and 24 and their eccentrics 25 and 28, on the shaft 22, and the gears 25 and 27 and their eccentrics 3B and ti on the shaft 25. The eccentric straps 32, 35, 35 and :55. being connected through the linkage mechanisms 35 to the outer slide connection links 3?, operate the bell cranks 54, links 58, bell cranks 55, links 53, bell cranks 55, links 58 and the bell cranks is. The bell cranks 12 are, therefore, caused to oscillate on their shafts II. This oscillatory movement of the bell cranks In pulls, the links 31 in downward direction froni the position shown in Fig. 1, to the lowermost clamping position shown in Fig.8. The continuous rotation of the eccentrics on the-shafts 22 and 25 causes the outer slide linkage mechanisms 35 to move the connection links 3'3 and consequently the outer slide 38, the outer slide 38 moving from the position shown in Fig. 1 to the position shown in Fig. 9 and then back again to the original initial position shown in Fig. 1, whereby one complete cycle of opera-p tion is completed.

Inner slide 53 and linkage mechanism 51 The eccentric straps 4'5 and its on the shaft 22,

and the eccentric straps t9 and 58 on the shaft 25 operate the inner slid-e connection links 52 to reciprocate the inner slide 53 in upward and downward directions, Figs. 1, 5 and 11. The inner slide 53 is suitably guided in guides carried by the outer slide 38 and is adapted to recipro cats in and with respect to the outer slide.

These eccentric straps 51, d3, 48 and 50 each operate an inner slide connection link 52. There is an inner slide connection link 52 at each of the corners of the inner slide, and they are pivotally attached to the inner slide 53 at their upper ends. The rotation of the gears 39 and and their eccentrics 4'! and 48 on the driven shafts 22, and the gears 4! and 42 and their eccentrics 49 and 5!? on the shaft 25, cause operation of the inner slide linkage mechanism 5!. The inner slide mechanism 5! operates the inner slide connection links 52 which, in turn, cause vertical reciprocation of the inner draw slide E33.

Each linkage mechanism 5!, Figs. 1, 5 and 11, for each inner slide connection link 52 comprises a bell crank '54, Figs. 1, 5, l and 11, which is pivotally mounted on the outer slide connection pin '72. One arm, or part, of the bell crank M is pivotaliy connected at '55 to an appropriate inner slide eccentric, the other arm, or another part, of thebell crank "it being pivotally connected. at to the lower end of an inner slide connection link 52. The upper end or" each link 52 is mounted on a pivot pin ll carried by the inner draw slide 53, Figs. 1, 4, 9 and 11.

The inner linkage mechanism for each inner slide connection link 52, from the point Where the link 52 connects with the bell crank it to the point 75 where the bell crank is pivotally connects to an inner slide eccentric strap, is identical, there being linkage mechanism 5! connected to each eccentric strap 4?, AS, ilk and to oper ate a respective inner slide connection link 52, Figs. 1, 5, 9 and 11. The linkage mechanisms 5!, are identical in construction, there being two such linkage mechanisms 5! on the right hand side of the press, and two such linkage mechanisms on the left hand side of the press, Fig. 5. The positioning of the right and left hand linkage mechanism 5-i is clearly shown in Fig. ll. These right and left hand inner slide linkage mechanismsare duplicated, there being a pair at the front and a pair at the rear, making a total of four such linkage mechanisms, Fig. 5. The size, shape, construction and pivotal con nections of the parts forming the linkage mechanisms 5|, from the point where the inner slide connection links 52 connect at '58 to the point '55 where the bell crank it is connected to its respective eccentric strap, are identical; therefore, the inner slide linkage mechanism having been de scribed with respect to one inner slide connection link 53. it is unnecessary to describe again e the i ka ehe sms 5 for ea i k 52-.

Operation of the eccentric straps gll, 4 8,: 4? and 59 will cause movement of the inner slide wi i -$19 l ll .3-, 1 ens quen l r i ocate the i r s de un fire an qwn rel Fig. l shows the inner slide 5;} at its uppermost position, and Fig. 9 discloses the position of the inner slide 53 just before the beginning of the metal drawing operation and at the time the outer slide is at its dwell and clampil position; while Fig. 11 shows the inner slide 53 at the com; pletion of the metal drawing operation. The inner slide 53 therefore is caused to reciprocate from the position shown in Fig. 1 to the'position shown in ll and then back to the position shown in s- 1 o om te ens W ep' o he n r de 53 an he er heet are driven by the driven shafts 22 and 25, the inner slide and outer slides will operate together and in proper timed relation with each other, The construction, arrangement and location of the linkage mechanism St for the outerslide and the linkage mechanism 53 for the inner slide 53, is such that both slides 33 and iii will move downwardly from the initial upper positions shown in Fig. l,to a position where the outer slide 38 will clamp a work piece iii, Figs. 1 and 9, against a part of a lower female die is? mounted on the press bed 2. The inner slide 5 carries a male forming die 8 which is adapted to cooperate with the female die This maledie 88 will not quite engage the metalblank T8 to be operated upon when the outer clamp slidefit is at dwell position, Fig. 9. The linkage m thanisms 36 and iii are so constructed and arranged that there W111 be a dwell oftfhe' pute'rsl-ide is when the outer slide clampingly' engages the metal blank it and during" the time the inner slide 53 operates to perform the metal drawing operation. After the outer .slide has engaged and clamped the metal, andw-hilethe outer slide is now dwelling, the inner slide continues downwardly to the positionof Fig. ll to effect the metal drawing operation.

It is desirable and necessary that there be a proper dwell of the outer clamp slide 38 to permit the work piece 78 to be securely and'rigidly h eld in place on the lower die 19 while the metal draw ing operation is being done by the innerdraw slide 53. It is also necessary and desirable that the inner draw slide move upwardly before movement of the clamp slide 3 8 so as to free the dies 19 and 80 and the finished article ,whereafter both slides move upwardly together to permit the finished work piece to be removed frombetween the dies 19 and so.

Bell crank construction for linkage mechanisms 36 and 51 linkages 3 6 are all similarly constructed like the bell crank 10, Fig. 1.0, and, thereforefonlythe bell crank 10 will be described.

The bell crank 19, Fig. 10, comprises spaced, properly shaped plates 8] and ,82 which are in.- tegrally connected together by a central hollow hub 83 extending therebetween. The shaft 1!. which carries each bell crank 73 passes through the hollow hub 83, whereby the bell cranks H! are pivotally mounted on the shafts H. The links 31 and 68 which are connected to the bell crank 10 are arranged between the spaced side plates 8| and 82 and are pivotally connected by the pins 12 and 69 to the spaced plates 81 and 82.

The bell crank '14, Fig. 10, of each inner slide linkage mechanism comprises a pair of spaced plates 84 and 85 which are maintained in spaced relationship by a hollow hub 86 pivotally mounted on the outer slide connection pin E2. The inner slide connection link 52 is arranged between the plates 84 and 85, and the pivot pin 73 passes through the plates 84 and 35 and the lower end of the link 52. Each of the respective inner slide eccentric straps 4?, 48, 5.9 and 5B, is arranged between the plates 84 and 85 of the corresponding bell crank 74 connected thereto by the pin 15, the eccentric strap 68 being shown in Fig. 10.

Each bell crank ill for the outer slide, and the adjacent bell crank '14 for the inner slide are connected together by a pin 12, that is, the pins 12 form a pivotal connection between the respective bell cranks m and the bell cranks 14 adjacent thereto. The bell cranks l3 and the bell cranks M are maintained in spaced apart relationship by means of a spacer 8'! on the pin 12, Fig. 10.

In order to assure the proper synchronism and corelation between the inner draw slide 38 and the outer clamp slide 53, the mechanisms for operating each of said slides are tied together to assure proper uniform operation in the proper desired and necessary sequence.

Correlation between outer clamp slide 38 and inner draw slide 53 Each of the bell crank members Hi, to which the inner slide connection links 52 are secured, and which are operated by the eccentric straps 41 to 50, is operatively connected to the adjacent bell crank 10. Each bell crank 74 is pivotally mounted on and carried by the pin '52 to which the corresponding outer slide link 31 is pivotally connected. Each outer slide link 37, therefore, is thus operatively controlled by the pin E2 to which an inner slide link 52 is secured. Therefore, the bell cranks H3 to which the outer slide links 3'! are connected and by which these links 31 are operated, also causes the operation or shiftable movement of the bell crank memberl l to which the inner slide links 52 are secured.

Operation of linkage mechanisms 36 and 51 the outer slide links 37 and the inner slide links 52 Rotation of the shafts 22 and 25 causes rotation of the gears and the eccentrics onthese shafts. The eccentrics on these two shafts cause operation of the respective eccentric straps. The eccentric straps, therefore, cause operation of the various links, the various components of the linkage mechanisms 36 and El being initially disposed in accordance with the locations and positions shown in Fig. l, and the outer slide 38 and the inner slide 53 being at the uppermost end of travel before the beginning of their respective downward strokes. The operation of the gears on the shafts 22 and 25, therefore, causes the bell crank members it to shift slightly outwardly because of the movement of the inner slide eccentric straps. The inner slide 53 is first given a slight upward movement, whereupon the lower edge of the inner slide will be slightly above the lower edge of the outer slide during the beginning of the downward stroke. The continued opera-v tion of the eccentric straps then causes the outer ends of the bell cranks i l, and the outer ends of the bell cranks 10, to move inwardly, pulling both the inner slide 53 and the outer slide 33 downwardly. This downward movement of both slides 53 and 38 continues until the outer slide is in clamping engagement with the work piece 78 which is supported on the female die 19 on the press bed. The linkage mechanisms 36 and 5! and the connecting links 3'! and 52 for both the outer slide 38 and the inner slide 5! are thus in the positions shown in Fig. 9, with the inner, slide free to be operated by movement of the bell crank members 74 without in any way affect-, ing the movement of the outer slide linkage 36. The inner draw slide 53, therefore, is free to be pulled down by the inner slide eccentric straps -53 whereby the male die on the inner slide 5| will draw the metal of the workpiece 18 into the cavity of the female die. This metal drawing operation continues until the inner slide 53 reaches the position of Fig. 11. Continued rota'- tion of the bull gears on the shafts 22 and 25 then causes the respective bell crank members l4 and ill to shift on their pivots or aXes and raise the inner slide 33 and outer slide 53 upwardly from the positions shown in Fig. 11 to the original initial positions shown in Fig. 1.

The tieing together of the outer slide linkage mechanism 35 and inner slide linkage mechanism 5! is such that the outer slide 38 and inner slide 53, will first move downwardly together, until the outer slide 38 dwells and clamps the metal blank or work piece ill in fixed position against the female die 19. While the work piece is being so held by the outer slide 38, the inner slide 53 will move downwardly to affect the drawing operation. During such clamping engagement, the operation of the inner slide eccentric straps 4'l5ll, whichoperate the inner slide 53, will actuate the inner slide connection links 52 only, as the outer slide connecting links 31 will not move, even though there may besome slight movement of some of the component parts of the linkage mechanisms 36. Therefore, the outer slide will be maintained in clamping position, while the inner slide will be free to continue downwardly to effect the metal drawing operation Without in any way affecting or. operating the outer slide 38. At the conclusion of the metal drawing operation, the inner slide 53 vwill first move upwardly a slight distance, whereupon the linkage for the outer slide33 will be brought into operation. Both slides 33 and 53 will-then move upwardly until they reach the limitsof their upward travel, namely, the initial positions shown in Fig. 1. At the conclusion of the upward travel of both slides, a new metal b1ank 'i8 is inserted in position and the operation is again continued.

It has been found that the construction em,- ployed in the slide operating mechanisms em bodied in the present invention will ermit a considerable number of cycles of operation to be performed within a given time limit. The number of actual operating cycles per unit of time is considerably greater than is possible with mechanical presses employing the crank construction as commonly used; this is true even though the speed of travel of the inner slide 53, in performing the actual metal drawing opera-j tion, might be slightly less than the speed of the inner slide in conventional mechanical crank 1'1 perat d. presses. duri the drawin op rati n. as the shif g. r oth of he. sli simu t ne Qu ly, and y he. iein ether of the operatin l nkage mechanisms of b t sl des, a reater number f perating cycle p r iven time ca be obtained. For instance. in the conventional press above referred to, fo a drawing depth of twelve. inches, there must. be an over-all travel oi the crank of more than two feet, because the inner draw slid .3. must move downwardly one foot. tov perform, the drawing operation and then mov m r than. wo. fe pw rdly to permit the completed work to be withdrawn .flomv between, the. dies 19, and 80.. For a two-foot overll movement. there would have. to. be. a periph ral mo ement of a rank. of pi, which woul be a otal p r pher l m v e t 6- 832 fe t, and inasm ch as. the maximum drawing speed of the pres nt conventi nal sheet. st el now n rmally used is 60 feet per minute, there could only be bout. 9.5.4 cycles of operat on p mi ut Should the speed of operation of anordinary crank be increased, it would exceed the, metal flowing or drawing action, of the sheet steel. The increased speed would cause the sheet steel to rupture, crack. or otherwise become, deformed. In, any eve t.v he speed of the draw may never ex e d the drawing-capabilities of the metal, which is appr xim te y .0 f et pe mi ute, b cause f the nature, elast city and other characteristi s of. the

' heet. metal is. l mited- Sho ld t speed of the crank be. in eased. it. wou d exceed the s eed a which he present metal may be drawn. The pre ent con truc ion permi s. the number of c mplete cycles. of operation to be increased. because the speed of travel of both slides can be increased Without exceedin the draw limit of the metal o. he terme The. invention therefore permi s he metal. o be awn at the-p per peed, but

perm ts he. number o cycles. per minut to. be increased. T erefore. a press embodying th present design and construction can practically dou le the output r produ tion ov r pre n mechanical crank. operated presses.

' Acomparison oi the. operation of the press 01: the present invention with the operation of a conventional crankoperated m chanical press is gra h c l y ll strat d in .Figs- 2 and 1.3.

plete. cycle, i operatio oi a nventional press.

V its ini ial. position'th clamp slide mov s downward. twe ty-six inches un l. it clamps th blank in position. The draw slide moves downward twenty-onev inches. from its. uppermost p ition to rive. at thelblank- This. point Where the draw slide. first ga es th lank. s ndicated. i Pie. by he etter-A, The/draw. lideth n moves tw lve. in es. f rther to effe t a; twe ve inch. met draw; the lowermost p sition'of the draw slide being indicated in Fig. 12 by the letter B The metal drawing operation f e. conventional. press. as shown in its occurs between point, A and point B. It may be noted that, the length of time required for the draw slide to move from point A to. point B. is approximately 1.5. seconds. It. should also be noted that the. time duration for one complete cycle of operation of, the conventional. press is ht sec nds.

Fig, 13 shows, the clamp slide motion. curve and the draw slide motion curve for one c m.- pl te, (23 8. of, operation of, the press of the. pres ent. invention. The, clam-p slide moves downward twenty-six inches until .it clamps the blank 1g in position. The draw slide moves downward. thirty in hes un il it arrives at the blank, the. point where the draw slide first, arrivesat or engages the blank being indicated. by the, letter A. The. draw slide then moves twelve inches farther to effect a twelve inch metal draw, the lowermost position reached by the draw slide. being indicated by the letter B. It may be noted that the time required for the metal drawing operation is approximately 1.5' seconds, whereas, the duration of a complete cycle of operation is live seconds as compared with: the. eight seconds required for complete cycle of operation f press. stroke of the press of the present invention is greater, the total time for one cycle of operation is less, being five seconds, as against eight seconds for the conventional crank operated press. 1 The time required for the actual metal drawing operation is practically the same. for both presses, but the time required for the. movements of the clamp slides and draw slides to. and from metal drawing position is considerably faster for the press ofthe present. invention; therefore, the drawing operation accomplished by the press of the present inventionv is within. the limits of the. drawing capabilities of the metal, but the number of cycles of operation per minute is considerably increased. Another means for arriving at the increased humher .1 cycles of operation per minute is. disclosed and claimed in the application of William E. Wardr Serial No.-1'77,983, filed August 7, 19.50..

Guides for outer slide 38 ing leg 89- which-terminates in an inner inclined face Sil. The face 9b of each guide member 88. is adapted, to co-operate with an inclined lace 9!, on. a projection 92 on the. cross. members 9-3, 9.3. of the outer slide 38..

bers 33 and 92, respectively, prevent shifting of the outer slide 338 within the main frame l and maihtain'the outer slidein proper vertical slid ing position withrespect to the main frame l.

The guide faces on the members 88 and the guidefaces or surfaces-9i on the members 92 of t-he outer slide, preferably extend from the top to the bottom of the main frame I and the outer slide 38, respectively. The outerslide 38 is therefore properly guided within the frame I of the press.

Guides for inner slide 53 The inner slide 53 is mounted within the confilles of, the outer slide 38. The outer slide is provided with a. central opening 9d through is prevented by the guides 9.2 On the outer slide the conventional crank operated lfherefore, even though the draw slide The COfOP-r cratin and aligned faces as and 9! of the memwhich terminate in guiding faces 91 engaging guide strips 98 on the inner slide, four such pairs of guiding members 91 and 98 being provided, there being two pair of guides at the rear and two pair of guides at the front, as clearly shown in Fig. 2. The inner slide, therefore, is guided within the outer slide by the co-operating engagement of the members 05 and 95 and the members 91 and 98. These guides preferably extend throughout the entire length of both slides so as to guide effectively both slides throughout the entire movemnt of the inner slide.

Inner and outer slide adjustments The inner and outer slides are adapted to be shifted closer to or farther away from the lower die which is mounted on the bed of the press, according to the movement these slides are to have with respect to the particular drawing or metal forming operation. The inner slide and outer slide may each be automatically adjusted according to the character of work being drawn and the depth of the drawing. The adjustment of each of the slides is accomplished by shifting the slides vertically with respect to the slide connection links.

The inner slide 53 is adapted to be adjusted vertically by an electric motor 09 mounted on an upper surface of the inner slide 53. The motor 99 carries a pinion I on the motor shaft which engages a gear IIII (Fig. 2) on a transverse drive shaft I02. This drive shaft I02 carries a drive gear I03 on each of its ends and these gears I03 mesh with gears I04 spaced on opposite sides of the gears I03. The gears I04 are each fixed to a shaft which carries and drives a bevel gear I05. These bevel gears I05 mesh with bevel gears I06, there being a bevel gear I00 for each inner slide connecting link 52, Figs. 2 and 4. Each bevel gear I06 is fixedly secured to a. nut I01, Fig. 4, which is held against vertical movement by a retaining member I08. The gear I06 and the nut I01 are, however, free to rotate.

screw I09. Each adjusting screw I09 is secured to the upper end of a pin II passin through spaced jaws at the lower end of the adjusting screw I09 and through the upper ends of the connecting link 52. Therefore, as the shaft of the motor 99 rotates, the bevel gears I06 and their companion nuts I01 will also rotate, but inasmuch as vertical movement of the nuts I0! is prevented by the retaining members I08 fixed to the top of the inner slide 53, the adjusting screw I09 will be tran lated vertically and therefore cause the inner slide 53 to be translated downwardly or upwardly, depending uponthe rotation of the nuts I01. The four bevel gears I00 are all rotated at the same time during the rotation of the shaft I02 by means of the motor 99, and therefore, the same amount of movement will be effected with regard to each of the links 52 whereby the inner slide will be translated vertically.

The means for effecting the vertical adjustment of the outer slide 38 is accomplished in the same manner as the inner slide adjustment. Such means for effecting the outer slide adjustment comprises worm gears III, Figs. 2 and 4, which also carry nuts IIZ fixed to the top of the outer slide by retaining members H3. Adjustment screws I I4 threadedly engage each nut I I2. Each of these screws H4 is connected to a link 3'! by means of a pin I3 passin through the lower bifurcated end of the screw I I4 through an open- The nut I0! is thread-' edly engaged with the threads on an adjustin 14 ing in the upper end of the link 31. Each worm gear III is driven by a worm II6 mounted on a shaft H1. The shafts II1 are each driven by a pinion II8 on the shaft of an electric motor II9 which is fixed to the outer slide 42. The pinion I I8 meshes with a gear I20 on a transverse shaft I2I, Fig. 2. The shaft I2I causes the operation of the WOrm shafts II'I by means of gears and shafts as clearly shown in Fig. 3. Operation of the motor H0 therefore causes each worm gear I II to be rotated the exact same amount and inasmuch as the threads on the nuts H2 and the adjusting screws II4 are all the same, the outer slide 42 is moved upwardly or downwardly with respect to the bed of the machine.

A clutch I22 is employed between the motor and main drive shaft as shown in Figs. 4 and 5.

The clutch I22 is the only one required or necessary to cause both slides to be operated from a single source of power which is the main drive motor 9. Separate clutches for the separate slides, therefore, is overcome, there being but one motor and one clutch provided for operating and controlling the operation of both slide and the mechanism which operates them.

Rsum

The invention provides a mechanically operated press, particularly of the double action type, in which is embodied an outer clamp slide and an inner draw slide. Linkage mechanisms are provided in the press for first moving the outer clamp slide into clamping engagement with a metal blank or work piece. Other linkage mechanisms are provided for moving the inner draw slide so as to draw part of the work piece or blank into a female die while the said work piece is being clamped against the die by means of the outer clamp slide. The linkage mechanisms for the outer clamp slide and the inner draw slide are tied together in a manner such that the inner draw slide will move downwardly with the outer clamp slide until the outer clamp slide engages the metal blank or work piece. While the linkage mechanisms for the outer clamp slide are causing the said clamp slide to dwell inclamping position against the blank or work piece, the linkage mechanisms for the inner draw slide will operate in a manner such as to cause the draw slide to move further than the clamp slide'and thus perform the metal drawing operation. While the operating means for the linkages has been illustrated herein as being eccentrics, it will be obvious that equivalent means, such as a crank, could be used, and the term eccentric as used in the claims herein is intended to include the equivtion for the purpose of setting or adjusting the relative positions of the inner and outer slides for various kinds of metal drawing operations. It is desirable that the bed of the press and the metal forming die be located at or near the bottom of the press, with the inner and outer slides located at or near the top of the press. The invention, however, contemplates the reversal of parts so that the stationary bed will be above the clamp slide and the draw slide. In this latter arrangement the metal blank or work piece would have to be supported on the clamp slide and V r and as previously described.

then moving the clamp slide upwardly towards an upper bed and die, and then moving the draw slide upwardly to effect the drawing operation, but having the opera-ting mechanism including the slide connection links 3! and 52 and the.

linkage mechanisms 36 and El positioned in the lower part of the press. Such a construction would be indicated by inverting Figs. 9 and 11 of the drawings for the positioning of the slides, and employing the mechanism in the same manner as shown in Figs. 9 and 11 with respect to the driving mechanisms as shown when the drawings are in the normal position. It has been found desirable and practical, however, to locate the linkage mechanisms for the clamp slide and the draw slide beneath the fixed base, and to move the slides downwardly from an upper position, as shown in the various views Changes may be made in the form, construction and arrangement of the parts without departing from the spirit of the invention or sacrificing any of its advantages, and the right is hereby reserved to make all such changes as fall fairly in the scope of the following claims. The invention is hereby claimed as follows: 1. A mechanical press comprising a frame structure including a. bed, a female die memberinterconnecting said rocker arms, said links, and

said rocker arms interconnecting the clamp slide eccentric with the bell crank, a clamp slide link, int'e rconnectingfsaid bell crank with the clamp slide, said clamp slideeccentric and. said bell crank, rocker arms and links being so. arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide into clamping engagement with the article to be shaped on the female die member and then cause the clamp slide to, dwell so as to hold the said article-on the female die member, a second bell crank pivotally mounted on the first said bell crank at a point, thereon spaced from the pivot of said first bell crank to the frame structure, means connecting one arm of said second bell crank to said draw slide eccentric, and a-draw slide link interconnecting the draw slide with the other arm of said second bell crank, said eccentrics being angularly offset from each other so that operation of the clamp slide eccentric will move both slides toward the bed, bringing the clamp slide into clamping position and causing the same to dwell, and so that effective operation of the draw slide eccentric to effect the drawing operation of the draw slide will occur during the dwell of the clamp slide.

2. A mechanical press comprising a frame structure including'a bed, a clamp slide slidably mounted on the frame structure, a draw slide slidably mounted in the clamp slide and movable with respect to the clamp slide, a clamp slide eccentric and a draw slide eccentric, both of said eccentrics being mounted on a common .drive shaft, a bell crank pivotally mounted on the frame structure, a plurality of rocker arms pivotally mounted on the frame structure, links interccnnecting said rocker arms, said links and said rocker arms interconnecting the clamp slide eccentric with the bell crank, a clamp slide link interconnecting said bell crank with the clamp slide, said clamp slide eccentric and said bell crank, rocker arms and links being so arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwellyasecond bell crank pivotally mounted: on the first said bell crank at a point thereon spaced f-rom the pivot of said first bell crank to the frame structure,

means connecting one arm of said second bell crank to said draw slide eccentric, and a draw slide link interconnecting the draw slide with the other arm of said second bell crank, said eccentrics being angularly offset from each other so that operation of the clamp slide eccentric will move b oth slides toward the bed, bringingthe clamp slide into clamping position and causing the same to dwell, and so that eifective'operatiqn of the draw slide eccentric to effect the drawing operation of the draw slide will occur during the dwell of the clamp slide. 7 Y

3. A mechanical press comprising a frame structure including a bed, a clamp slide slidably mounted on the frame structure, a draw slide slidably mounted in the clamp slide and movable with respect to the clamp slide, a clamp slide eccentricand a draw slide eccentric, common drive means for said eccentrics, a rocker member pivotally mounted on the frame structure, a plurality of rocker armspivotally'mounted onthe frame structure, links interconnecting said rocker arms, said links and said rocker arms interconnecting the clamp slide eccentric withthe rocker member, a'clamp slide link interconnecting said rocker member with the clamp slide, said clamp slide eccentric, rocker member, rocker arms andlinks being so arrangedjand coordinated with respect to eachother that operation of the clamp slide eccentric will bring the clamp slidev to clamping position and then cause the clamp slide to dwell, a second rocker member pivotally mounted on the first said rocker member at a point thereon spaced from the pivot of said first rocker member to the frame structure, means pivotally connecting said secondrockermember to said draw slide eccentric, and a draw slide, link interconnecting the draw slide with said second rocker memben'said eccentrics being maintained in. a predetermined angular relationship from slide eccentric and a draw slide eccentric, common drive means for said eccentrics, a rocker member pivotally mounted on the frame structure, linkage means interconnecting the clamp slide eccentric with said rocker member, at least one of the links in said linkage means being pivotally mounted on the frame structure, a clamp slide link interconnecting said rocker member with said clamp slide, said clamp slide eccentric, rocker member, linkage means and clamp slide link being so arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second rocker member pivotally mounted on the first said rocker member at a point thereon spaced from the pivot of said first rocker member to the frame structure, means connecting said second rocker member to said draw slide eccentric, and a draw slide link interconnecting the draw slide with said second rocker member, said eccentrics being maintained in a predetermined angular relationship from each other so that operation of the clamp slide eccentric will move both slides toward the bed, bringing the clamp slide into clamping position and causing the same to dwell, and so that effective operation of the draw slide eccentric to effect the drawing operation of the draw slide will occur during the dwell of the clamp slide.

5. A mechanical press comprising a frame structure including a bed, a clamp slide slidably mounted on the frame structure, a draw slide slidably mounted in the clamp slide and movable with respect to the clamp slide, a clamp slide eccentric and a draw slide eccentric, common drive means for said eccentrics, a bell crank pivotally mounted on the frame structure, operating means connecting said clamp slide eccentric with said bell crank, a clamp slide link connecting said bell crank with said clamp slide, said clamp slide eccentric, bell crank, operating means and clamp slide link being so arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second bell crank pivotally mounted on the first said bell crank at a point thereon spaced from the pivot of said first bell crank to the frame structure, means connecting said second bell crank to said draw slide eccentric, and a draw slide link connecting said second bell crank with said draw slide, said eccentrics being maintained in a predetermined angular relationship from each other so that operation of the clamp slide eccentric will move both slides toward the bed, bringing the clamp slide to clamping position and causing the same to dwell, and so that effective operation of the draw slide eccentric to effect the drawing operation of the draw slide will occur during the dwell of the clamp slide.

6. A mechanical press comprising a frame structure including a bed, a clamp slide slidably mounted on the frame structure, a draw slide slidably mounted in the clamp slide and movable with respect to the clamp slide, a clamp slide eccentric and a draw slide eccentric, drive means for said eccentrics, linkage means connecting said clamp slide eccentric with said clamp slide, including a link pivotally mounted on the frame structure, said linkage means being so arranged and coordinated that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second linkage means connecting said draw slide eccentric with said draw slide for effecting a drawing movement of the draw slide including a link pivotally mounted on said first link at a point thereon spaced from the pivot of said first link on the frame structure, the arrangement of said linkages being such that operation of the first said linkage means will operate said second linkage means for moving said draw slide, said eccentrics being maintained in a predetermined angular relationship from each other so that operation of the clamp slide eccentric will move both slides toward the bed, bringing the clamp slide to clamping position and causing the same to dwell, and so that effective operation of the draw slide eccentric to effect the drawing operation of the draw slide will occur during the dwell of the clamp slide.

RUDOLPH W. GLASNER. EINAR K. JOHANSEN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 564,990 Good Aug. 4, 1896 1,986,410 Rode Jan. 1, 1935 2,071,001 Rode et al Feb. 16, 1937 

